FR2504626A1 - CLUTCH STOPPER, PARTICULARLY FOR A MOTOR VEHICLE CLUTCH - Google Patents

Abstract

THIS STOP HAS AN AUTOMATICALLY CENTERING CLUTCH BEARING 1 ARRANGED ON OR IN A SLIDING SLEEVE 2, THE FIXED RING 3 OF THE CLUTCH BEARING BEING COUPLED WITH THE SLIDING SLEEVE 2 BY AN INTERMEDIATE ELEMENT 9, 15, 24, 32, 38 , 47, 53, 63, 70 WITH GUIDES FOR THE RADIAL DISPLACEMENT OF CLUTCH BEARING 1 IN RELATION TO SLIDING SLEEVE 2 IN TWO PERPENDICULAR RADIAL DIRECTIONS. THE INTERMEDIATE ELEMENT 9, 15, 24, 32, 38, 47, 53, 63, 70 IS RADIALLY PRE-STRESSED AGAINST THE FIXED BEARING RING 3 AND THE SLIDING SLEEVE 2 IN TWO CROSSING DIRECTIONS.

Description

CLUTCH STOP, PART ICJ L EREMENT FOR A: CLUTCH OF

MOTOR VEHICLE

  The present invention relates to a clutch stop

  age, especially for a vehicle clutch

  mobile, in which a self-centering clutch bearing

  matic is placed on or in a sliding sleeve and the fixed ring of the clutch bearing is coupled by a

  intermediate element with the sliding sleeve which

  carries guides for the radial displacement of the bearing

  clutch in relation to the sliding sleeve, in two directions

radial crossings.

  Patent DE AS 16 00 080 has already described a bearing

  self-centering clutch to the clutch which

  te a spring exerting its force on the fixed bearing ring

  in the axial direction of the bearing support This arrangement

  known position has the disadvantage that the spring acts

  health in the axial direction produces very high damping

  the radial movement of the bearing, so that the center

  automatic clutch bearing adjustment is considerable-

  and is only possible after a certain number of disengages. It is also known from patent DE OS 2 156 161 to avoid any rotation relative to the sliding sleeve of a clutch bearing pushed in the axial direction by a spring, by a mechanical locking, in which case an intermediate element is provided. with two guides arranged in a cross which cooperate with the fixed bearing ring and the sliding sleeve This clutch stopper has the disadvantage that to prevent rotation of the fixed bearing ring and for the axial positioning of the bearing on

  the thrust collar of the sliding sleeve,

  separate components are required and that automatic centering

  only from the clutch bearing by the axially acting spring

is difficult.

  The object of the invention is therefore (to perfect it a clutch stopper of the type described in the preamble, so that the large radial movements of the clutch bearing can be absorbed without the automatic centering being practically disturbed. In addition, the number of parts must be reduced and the assembly of the clutch bearing

be simplified.

  In a clutch bearing according to the invention, this result is obtained by the fact that the intermediate element is prestressed radially against the fixed bearing ring and the sliding sleeve, in two directions which intersect.

  Thanks to this arrangement of two guides that cross

  feeling and radial prestressing of the intermediate element

  diary with the fixed bearing ring and the sliding sleeve

  the clutch bearing can move in either direction

  tion radially and center exactly without great compressive force relative to the ends of the tabs of the

  clutch diaphragm spring, the relative movement of the pa-

  link the clutch with respect to the sliding sleeve in each

  that position being amortized According to another characteristic

  of the invention, the fixed bearing ring has an opening

  ture with two guide surfaces parallel to each other

  between which is a poly-shaped spring ring

  gonal provided with two pairs of parallel sectioms between

  and perpendicular to each other, the surfaces ex-

  lower sections of a pair coming to rest on the

  opening guide surfaces and interior surfaces

  res of the sections of the other pair coming to bear on the sur-

  outer face of the sliding sleeve with a radial preload.

  According to another advantageous characteristic of the

  vention, an elastic plastic disc is available.

  axially seated between the thrust collar of the sliding sleeve and the fixed bearing ring, this disc having an opening with two diametrically opposite housings

  and guide surfaces parallel to each other, on the

  which are supported by the projecting parts directed axially-

  coupled with the fixed bearing ring In the opening

  two other guide surfaces are provided for the disc

  parallel to each other, offset by 900 with respect to the

  guide surfaces and which are supported in housings

250 462 d

  the outer surface of the sliding sleeve.

  Thanks to this configuration of the intermediate element

  in the form of a disc with corresponding guide surfaces

  This element can be manufactured in one piece by molding or injection without any other machining operation being necessary. Due to the characteristics of the material of the disc, the latter also provides

  damping of noise and oscillations.

  The intermediate element can also consist of a disc with four elastic tabs folded in

  the axial direction, these tabs being arranged parallel

  parallel between them two by two and formed on different faces of the disc The tabs offset by 900 are supported on one side with their guide surfaces on corresponding surfaces of the push flange

  sliding sleeve and, on the other side, on

  corresponding sides of the fixed bearing ring, with

  a prestressing In this arrangement, the element inter-

  medium is inexpensive to manufacture and allows assembly

simple from the clutch release bearing.

  Other features and advantages of the

  vcntion will appear during the description which will

  follow several examples of implementation and refer to it

  relating to the accompanying drawings in which:

  Figure 1 is a section A-B of a clutch stop

  age of Fig 3 with a self-centering clutch bearing

  matic and a circular cross-section spring ring

  ring as an intermediate element,

  Figure 2 is a section C-D of the thrust stopper.

clutch shown in Fig 3.

  Figure 3 is a side view of the left of the clutch release bearing according to Figures 1 and 2, without the balls and the inner ring, Figure 4 is a section of a variant of a

  clutch bearing according to the invention, with a ring-res-

  spell of polygonal shape and cross section rec-

  tangular, Figure 5 is a radial section of the clutch bearing shown in Fig 4, Figure 6 is an EF section of the clutch bearing shown in Fig 7, comprising a disc instead of a spring ring , Figure 7 is an axial section of the clutch bearing of Fig 6, Figure 8 is an axial section of a variant of a clutch bearing according to the invention, without the balls and the ring inside, Figure 9 is a left side view of the clutch bearing shown in Fig 8, Figure 10 is a partial section GH of Figure 9 Figure It is a section IK of the clutch bearing shown in Fig 13, in which the disc intended

  to adjust the radial displacement of the clutch bearing is

  placed inside the fixed bearing ring and rests on the thrust plate, Figure 12 is a LM section of the clutch bearing shown in Fig 13, Figure 13 is a left side view of the clutch bearing represented in FIG. 11, FIG. 14 is a section PQ of another embodiment of a clutch bearing according to the invention with a projecting part disposed on the fixed bearing ring s' engaging in a disc housing, FIG. 5 is a section N- 0 of the clutch bearing represented in FIG. 16, FIG. 16 is a side-left view of the clutch bearing of FIG. 14,

  Figure 17 is an R-S section of the clutch bearing.

  ge of Fig 18, in which the radial displacement is determined by a disc of cross section in Z, Figure 18 is a left side view of the clutch bearing of Fig 17, Figure 19 is a section of a clutch release bearing according to the invention in which the radial displacement of the clutch bearing is regulated by cylindrical pins,

  Figure 20 is a side view of the stacking stop

  clutch shown in Fig 19, without the balls and the inner ring,

  Figure 21 shows a variant-of-

  reading of a clutch release bearing according to the invention with an intermediate element of which projecting parts engage in cross housings of the fixed bearing ring and the thrust flange and FIG. 22 is a side view of the clutch bearing of figure 21 without the balls and the ring

interior.

  Figures 1 to 3 show a stop for em-

  clutch comprising a self-centering clutch bearing 1

  material which is arranged with a radial clearance on a sliding sleeve 2 The clutch bearing 1 comprises an outer ring 3 fixed in sheet metal which, by a ledge 4 directed

  radially inward, applies to a collar-

  pressure head 5 made in one piece with the sliding sleeve

  sant 2, a solid circular inner ring 6 and balls 6 a The outer ring 3 has, in the rim

  4, an opening 7 with two parallel guide surfaces 8

  between them, between which a ring is inserted

  spring 9 of polygonal shape, with a prestressed

  diale The ring-spring 9, of circular cross-section

  area, has two pairs of sections 10 and 11, each parallel and which are offset by 900 one relative to

  the other The outer surfaces 12 of the parallel sections

  lèles 10 apply with a radial preload on the guide surfaces 8 of the opening 7 The interior surfaces lla of the parallel sections It is one of

  the other at an interior distance which, in the unassembled state,

  wheat, is less than the diameter of the sliding sleeve 2

  in this region So, by overcoming an elastic force

  that, a displacement of the fixed bearing ring 3 on the surfaces 12 of the spring ring 9 in a radial plane X

  and a displacement of the outer ring 3 with the ring-

  spring 9 in a radial plane Y offset by 900, on the sur-

  outer face 13 of the sliding sleeve 2 are possible.

  This arrangement and this configuration the ring-res-

  t, fate 9 provides a possibility of radial adjustment damping the vibrations of the clutch bearing I in

  all directions, the radial position of the bearing

  clutch 1, which is established following an axial offset, remaining maintained even when the preload is absent or minimal The axial fixing of the clutch bearing

  1 on the sliding sleeve 2 is made by a thick washer

lée 14.

  In principle, the embodiment represented

  felt in Figs 4 and 5 is similar to that shown in Figs 1 and 3 The difference is simply that the spring ring 15 d (the polygonal shape has a rectangular cross section and is arranged in an opening 16 d '' a plate 17, for example in material

plastic.

  This plate 17 is introduced into the bore 18 of the outer ring 3 and bears against the surface

  interior 19 of ledge 4 In addition, in the region of an-

  spring-spring 15, the sliding sleeve 2 has a flat 20 on which the parallel sections 21 of

  the spring ring 15 of polygonal shape, with a pre-

  radial tread The sections 22 of the spring ring 15 are arranged on the guide surfaces 22 a of the plate 17 The maintenance of the plate 17 with the clutch bearing 1 on the sliding sleeve 2 is done by a thin ring

  23 which is held by a retaining ring 23 a.

  Figs 6 and 7 show a variant of

  Reading of the clutch release bearing according to the invention Instead of the ring 9 of polygonal shape, there is provided a

  3 disc 24, for example made of plastic, arranged axially-

  ment between the fixed bearing ring 3 and the thrust collar 5 of the sliding sleeve 2 As shown in Fig 6, the disc 24 has an opening 25 with

  two housings 26, diametrically opposed, the sur-

  guide faces 27 are parallel to each other On these guide surfaces 27 are supported axially directed projecting parts 28 which are made in one piece with

  the fixed bearing ring 3 In the unassembled state, the

  250462 distance A between the guide surfaces 27 of the housings 26 is less than the distance between the opposite surfaces 29 of the projecting parts 28, so that the disc 24 is

  pre-loaded on the projecting parts 28.

  In addition, in the opening 25 of the disc 24 are provided two parallel surfaces 30, offset by 900 relative to the surfaces 27 and which, in the unassembled state, are separated

  by a distance less than the diameter of the sliding sleeve

  health 2 in this region This provides a possibility

  lity of movement of the clutch bearing 1 relative to the disc 24 in a radial direction and a possibility of displacement of the clutch bearing 1 relative to the disc 24 in a radial direction offset by 900, so that

  in the case of a superposition of the two movements, a

  unobstructed radial setting of the clutch bearing 1 to reach

  dre a centered position relative to the clutch diaphragm spring (not shown) is guaranteed, this position also remaining maintained with a low or absent prior load The clutch bearing 1 and the disc 24 are fixed on the sliding sleeve 2 in the axial direction

by means of a retaining ring 31.

  Figures 8 to 10 show another alternative embodiment. In all its essential parts, this

  embodiment corresponds to that of the end stop

  clutch of Fig 6 and 7 The difference lies in the confi-

  guration of the disc 32 and of the fixed bearing ring 3 The disc 32 has protruding parts 33, each directed

  radially inward and snapping into each

  a protruding part 34 formed in an axial direction on the fixed bearing ring 3 in the region of its bore, so that the disc 32 and the clutch bearing 1 form a unit The guide surfaces 35 of the disc 32 s 'bear on the surfaces 36 of the protruding parts 34 while the guide surfaces 37 parallel to each other

  of the disc 32 cooperate with the outer surface 13 of the

sliding door 2.

  The embodiment shown in Fig it

  to 13 is also in principle similar to that of dice.

  the clutch release bearing in Figs 6 and 7 The difference is

  in that for the setting of the possibility of de-

  radial placement, the disc 38 is not disposed between the fixed bearing ring 3 and the thrust collar 5 of the sliding sleeve 2, but in the bore 39 of the fixed bearing ring 3, and is applied against the surface inner 40 of the rim 4 In this embodiment, the rim 4 of the

  outer ring 3 has an open 41 with two housing

  diametrically opposed elements 42, having guide surfaces 43 parallel to each other on which are supported

  protruding parts 44 of the disc 38 In the unassembled state

  wheat, the distance C between the guide surfaces 43 of the outer ring 3 is less than the distance between the opposed surfaces 45 of the projecting parts 44 The opening 1.5 4 la in the disc 38 has two parallel surfaces 46 which are offset by 900 in relation to the guide surfaces

  43 and which, in the unassembled state, are separated by a dis-

  tance D less than the diameter of the sliding sleeve 2 in

this region.

  In the clutch stop shown in Figs. 14 to 16, the fixed bearing ring 3 is supported by the flange 4 folded radially inwards on the flange of

  thrust 5 of the sliding sleeve 2 The disc 47 is also

  ment made like the disc 24 of Fig 6 and it has an opening 48 with two diametrically opposite housings 49, with guide surfaces 50 parallel to each other on which project protruding parts 51 projecting axially, coupled with the ring fixed bearing 3 in the region of the bore In addition, in the opening 48

  disc 45 are provided two parallel guide surfaces 52

  those which are offset by 900 relative to surfaces 50 and whose distance in the unassembled state is less than

  diameter of the sliding sleeve 2 in this region.

  Figs 17 and 18 show another embodiment of a clutch release bearing according to the invention in

  which, between the thrust collar 5 of the sliding sleeve

  sant 2 and the rim 4 folded radially inwards from the fixed outer ring 3 is provided a disc 53 with 250462 d four tabs 54, 55 folded in the axial direction and elastic in the radial direction Two tabs 55

  diametrically opposed are folded towards the bearing

  clutch while the tongues 54 offset by 900 are folded away from the bearing The tongues 54 bear with prestress on surfaces 56 parallel to each other at the periphery of the thrust flange 5 while

  that the tongues 55 are arranged on guide surfaces

  dage 57 directed parallel to each other of two housings 58, which are formed in the bore 59 of the rim 4 directed radially inwards The width of the housings 58 is greater than the width of the elastic tongues 55 which allows movement of the ring fixed bearing 3 with respect to the disc 53 in a radial direction, while the fixed bearing ring 3 with the disc 53 can move in a radial direction offset by 900, the tongues 54 serving to guide the surfaces 56 of the flange 5 In the

  If the two movements are superimposed, the bearing

  clutch can undergo every necessary radial movement and it

  is fixed in the central position after the centering operation

  The axial fixing of the fixed bearing ring 3 with

  the disc 53 on the sliding sleeve 2 is made by a round

del The shouldered 60.

  In the clutch stop shown in Figs 19 and 20, the outer ring 3 rests by the flange 4 folded radially inwards on the thrust flange 5 of the sliding sleeve 2 The flange 4 and the thrust flange 5 each have cross notches 61, 62,

  the notches 61 of the fixed bearing ring 3 being vertica-

  the and the notches 62 of the thrust collar 5 being horizontal In each of the notches 61, 62 is introduced

  a cylindrical stud 63 whose diameter is slightly su-

  smaller than the width of the notches 61, 62 so that when the clutch bearing 1 is moved in the radial direction, a frictional force occurs on the pins

  cylindrical 63, keeping the bearing 1 in its position.

  Thanks to the cross arrangement of the notches 61, 62, the pa-

  Clutch 1 can take any position that precedes

  feel at the time of centering In the case of a vertical movement, only the bearing 1 moves while in the case of a horizontal movement, the bearing 1 moves with the pin 63 The axial fixing of the clutch bearing 1 on the sliding sleeve 2 is made by a disc 64 which

  engages in an annular groove 65 at the peri-surface

sliding sleeve 2.

  The embodiment shown in Figure 21 and Fig 22 differs from that of Figures 19 and 20, in that, between the flange 4 and the thrust flange 5, is interposed a disc 70, for example of plastic, which , by corresponding protruding parts 66, 67, engages in notches 68, 69 arranged in a cross in

  the push collar 5 and the flange 4, with a pre-

radial stress.

  The embodiments which have been described are only examples of clutch stops according to the invention. It is quite obvious that modifications to the individual elements are within the scope of the invention. For example, the spring ring of shown polygonal shape

  on Fig 1 and 3 can not only rely on the over-

  outer face 13 of the sliding sleeve 2, but can also engage in two notches on the outer surface of the sliding sleeve, parallel to the neighboring surfaces of the ring-spring 9 of polygonal shape, which allows by simple fixing of the spring ring 9 on the fixed bearing ring 3 by non-foldable tabs or the like, simple coupling of the clutch bearing with the sliding sleeve by the spring ring 9 The possibility also exists that the angle at which they intersect the guides

  for radial displacements of the clutch bearing with respect to

  port to sliding sleeve is not a right angle.

250462 i ll

Claims (9)

  1 clutch release bearing, particularly for a   motor vehicle clutch, in which a bearing   self-centering clutch (1) is arranged on or in a sliding sleeve (2) or the like, and the fixed ring (3) of the clutch bearing (1) is coupled by an intermediate element (9, 15, 24, 32 , 38, 47, 53, 63, 70) with the sliding sleeve (2) and comprising guides for the radial displacement of the clutch bearing (1) relative to the sliding sleeve (2) in two radial directions which intersect, clutch bearing characterized in that the intermediate element (9, 15, 24, 32, 38, 47, 53, 63, 70) is prestressed radially in two directions which intersect with the fixed bearing ring (3) and the sleeve sliding (2).   2 clutch bearing according to claim 1, characterized in that the intermediate element (9, 15, 24, 32, 38, 47, 53, 63, 70) is prestressed radially in a directed radial plane (Y) along the length of the median axis, for example on the fixed bearing ring (3) and in a plane (X) perpendicular to this plane (Y) on the sleeve sliding (2).   3 clutch bearing according to claim 1 or 2, characterized in that the fixed bearing ring (3) has an opening (7) with two guide surfaces (8) parallel to each other, between which is disposed a spring ring (9) made with a polygonal shape, this spring ring being provided with two pairs of sections (10; 11) parallel to each other and perpendicular to each other, the outer surfaces (12) of the sections (10) d 'a pair applying to the guide surfaces (8) of the opening (7) and the interior surfaces (11a) of the sections (11) of the other pair applying to the surface   outside (13) of the sliding sleeve (2) with a pre- radial stress.   4 clutch bearing according to claim 3, characterized in that the sliding sleeve (2) has two diametrically opposite notches, parallel to a 1 _ perpendicular to the axis, and in which engage by means corresponding the ring - form spring (9)   polygonal, coupled with the fixed bearing ring (3).   Clutch bearing according to any one of   Claims 1 to 3, characterized in that it comprises,   in the bore of the fixed bearing ring (3), a disc (17) with an opening comprising two guide surfaces   (22 a) arranged at a distance from each other, between the   which is arranged a spring ring (15) of poly-   gonal with at least two pairs of sections (21, 22) parallel   between them, and applying to a flat (20) of the sliding sleeve (2) and to the guide surfaces (22 a) of the disc (17).   6 clutch bearing according to claim 1   or 2, characterized in that it comprises, arranged axially-   between the push collar (5) of the sliding sleeve   sant (2) and the fixed bearing ring (3), a disc (24,32) for example made of plastic which has an opening (25) with two diametrically opposed housings (26), and 2 D of the guide surfaces ( 27, 35) parallel to each other, to which axially directed projecting parts (28, 34) are applied, coupled with the fixed bearing ring (3), the distance (A) between the guide surfaces (27, 35 ) housings (26) in the unassembled state, being   less than the distance between the surfaces (29, 36) op-   placed one on the other of the projecting parts (28, 34), two guide surfaces (30, 37) parallel to each other lying in the opening (25) of the disc (24, 32), these surfaces guide being offset by 900 relative to the guide surfaces (27, 35) and, in the unassembled state, their distance (B) being less than the diameter of the sleeve sliding (2) in this region.   7 clutch bearing according to claim 6, characterized in that the disc (32) has a projecting portion (33) directed radially inwardly which engages behind the projecting portions (34) formed outward in the axial direction on the ring fixed bearing (3).   8 clutch bearing according to claim 1 or 2, characterized in that the flange (4) of the ring   interior (3) has an opening (41) with two compartments   diametrically opposed elements (42), comprising guide surfaces (43) parallel to each other on which projecting parts (44) coupled to the disc (38) are applied, the distance (c) between the guide surfaces   (43) of the housings (42), in the unassembled state, being inferior   less than the distance between the surfaces (45) opposite one   to the other of the projecting parts (44), two surfaces parallel   leles (46) being provided in the opening (4 ia) of the disc (38) offset by 90 relative to the guide surfaces (43) and whose distance (D) in the unassembled state, is less than the diameter of the sliding sleeve (2) in this region.   9 clutch bearing according to claim i or 2, characterized in that the disc (47) has a   opening (48) with two diametrically op- posite housings (49)   laid comprising parallel guide surfaces (50)   between which apply with a precon-   radial tread of the projecting parts (51) coupled with the fixed bearing ring (3), the opening (48) of the disc (47) being provided with two parallel guide surfaces (52) which are offset by 900 relative to to surfaces   (50) and whose distance, in the unassembled state, is in-   smaller than the diameter of the sliding sleeve (2) in this region. Clutch bearing according to claim i   or 2, characterized in that, between the push collar   the disc (5) of the sliding sleeve (2) and the flange (4) folded radially towards the outside of the fixed bearing ring (3) is disposed a disc (53) with four tongues (54, 55) elastic in the direction radial, folded   in the axial direction, two tongues (55) diametra-   Lement opposite being directed towards the clutch bearing (1) and applying with a preload on guide surfaces (57) parallel to each other of two diametrically opposed housings (58) which are provided in the bore of the flange (4) , and two tabs (554) offset by 900 being directed opposite the clutch bearing (1) and   applied with radial prestressing on sur-   guide faces (56) parallel to each other with the outer surface of the thrust flange (5). Il Clutch bearing according to claim I or 2, characterized in that the flange (4) of the ring   fixed bearing (3) and the thrust collar (5) of the   sliding slide (2) each have two notches (61,   62) diametrically opposite, arranged in a cross, in the-   which is engaged a cylindrical stud (63) with a pre- radial stress.   12 Clutch bearing according to claim 1 or 2, characterized in that, between the flange (4) and the thrust collar (5) of the sliding sleeve (2) is disposed a disc (70) with projecting parts ( 66, 67) which engage with a radial prestress in notches (68, 69) arranged in a cross, of the flange of thrust (5) and rim (4).